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E. R- SMITH ETAL Aug. 9, 1932.

WORK HANDLING MECHANISM FOR momma; TOOLS Original Filed Jan. 28'. 1929 11 Sheets-Sheet. 1

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WORK HANDLING MECHANISM FOR MACHINE TOOLS Original Filed Jan. 28,- 1929 11 Sheets-Sheet 1o Aug. 9; 1932.

E. R. SMITH ET. AL

Re. 18,559 WORK HANDLING MECHANISM FOR MACHINE TOOLS I 11 Sheets-Sheet l1 iled 28, 1929 Original jgiaz R eis sued Aug. 9, 1932 UNITED STATES PATENT OFFICE '10 SENECA FALLS MACHINE OOKPANY, OI SENECA FALLS, NEW YORK, A CORPO- BAIION or massacnusmrs WORK HANDLING FOB MACHINE TOOLS Original. No. 1,s41,9aa, dated January 19, 1932, Serial No. 885,599, filed January 28-, 1929. Application for reissue filed February 29, 1982. Serial No. 595,953.

This invention relates to a machine tool and is shown embodied in an automatic lathe,

although not limited in its application to that particular type of machine. Such machine tools are coming into wide use for the ecofor feeding work to such a machine tool and for removing the finished work therefrom.

In the preferred form, our improved feeding mechanism is fluid operated and cam controlled.

A further object of our invention is to provide fluid operated work-supporting and work-driving mechanism operable in timed relation to said work-feeding mechanism and similarly controlled. Another object is to provide a fluid operated main driving clutch, so controlled that on failure to provide fluid pressure for actuating said work-feeding, work-supporting and work-drii'ing devices the main driving clutch will simultaneously become inoperative and all movements of the machine will cease.

Our invention further relates to arrangeinents and combinations of parts which .will be hereinafter described and more particularly pointed out in the appended claims.

' A preferred form of the invention is show in the drawings, in which Fig. 1 is a front elevation of an automatic lathe embodying our improvements;

Fig. 2 is a plan view thereof;

Fig. 3 is a diagrammatic perspective view,

showing the relation and driving connections for the various parts of the lathe; 4

Fig. 4 is an end elevation of the work-feeding mechanism, looking in the direction of the arrow 4 in Fig. 1;

Figs. 5, 6 and 7 are views similar to Fig. 4, but showing the parts in difi'erent relative positions;

Fig. 8 is a sectional elevation of one of the work-gripping devices and its pneumatic operating mechanism;

80 Fig. 9 is a sectional elevation of certain actuating mechanism, taken along the line 99 in Fig. 7;

Fig. 10 is a front elevation of the'workfeeding mechanism, looking in, the direction of the arrow 10 in Fig. 4:; y

Fig. 11 is a view similar to Fig. 8, but showing the parts in a different position;

Fig. 12 is a detail sectional view of parts of 'the gripper mechanism on an enlarged scale,

driving member, showing its co-operation with the work;

Fig. 21 is a sectional'plan view showing the co-relation of the head and tail centers and the work-driving member with the work;

Fig. 22 is a plan view of certain. pneumatic control mechanism;

Eig. 23 is a front elevationthereof, looking in the directionof the arrow 23 of Fig. 22";

, Figs 24 and 25 are sectional plan views, taken along the lines 24-24 and 2525 respectively in Fig. 23;

Fig. 26 is a sectional elevation of a certain piston valve mechanism, taken along. the line 26-26 in Fig. 22;,

Figs. 27 and 28 are sectional plan views, taken along the lines 27-27 and 2828 respectively in Fig. 26;

Figs. 29 and 30 are sectional elevations,'

showing the high and low'pressure air connections, taken along the lines 29-29 and.

30-30 respectively in Fig. 23; Fig. 30' is a diagrammatic sectional elevation' showing certain air-control connections I EDWIN B. SMITH AND ALBERT SCHINKEZ, OF SENECA FALLS, NEW YORK, ASSIGNOBS I .Figs. 31, 32, 33 and 34 are side elevations of the cams for operating the difierent control-valves for the pneumatic mechanism;

. ley 75, connect-ed by 'a pneumatic clutch 7.6-

Fig. 35 is a plan viewof the cam which operates the back tool slide;

F 36 is a side elevation of the cam and.

General construction Our improved lathe comprises a bed or frame 40 aving a head stock 41 and a tail stock 42. The head stock 41 is permanently secured to the bed 40 and the tail stock 42 is slidable on guideways 43 (Fig. fixed on the bed 40.

Our copending application 'Serial No.

401,555, filedOctober 22, 1929, is directed to the details of construction of the back tool slide and reference is made thereto for more specific information.

A front tool carriage 44 (Fig. 1) is slidable on ways 45 at the front of the bed 40 and is connected by a link 46 (Fig. 2) to an arm 47 (Fig. 3) having acam roll 48 engaged by a side cam 49 mounted on a main camshaft 50. A front tool slide 51 is mounted in guideways 52 (Fig. 1) in the carriage 44 and is moved to engage the work by a cam plate 53 secured on the bed 40.

The construction of the tool slide and the mechanism for actuating the same forms no part of our present invention and is fully disclosed in our prior application Serial No. 294,005, filed July 19, 1928.

A back tool "slide is also mounted in. guideways on a su port 61 which is adjustable lengthwise o the machine along the guideways 43 which support the tail stock 42.

For the purposes of this application it may be stated that the slide 60 is moved toward and from the work by a-cam 63 (Fig. 35) engaging a cam follower or roll 64 fast on the tool slide and asecond roll 65 yieldingly mounted on the tool slide.

The work W (Fig. 21) is supported at one end by the tail center and at its opposite or open end it is held against a conical end pprtion 73 of asupport 71, secured to the out end of the work driving spindle 72.

Dn'ving connections The mechanism for driving the work sup porting spindle 72, the front carriage cam 49 and the back tool slide cam 63 is illustrated diagrammatically in Fig. 3. a

Power is applied through a belt BQto-a pulto a main driving shaft 77. The shaft 77 is connected by gears 78 and 79' to a worm shaft 80 having a worm 81 engaging a worm wheel 82 on 'a shaftg83. The shaft 83 is con nected to the work spindle 72 by gears 84 and 85, thus positively rotating the workat constant speed. r

The main shaft 77 is also connected by spiral gears 8686 to a clutch 87 loose on a worm shaft 88.- The shaft 88 has a'worin 89 meshing with a worm wheel 90. The

worm wheel90is fixed on a shaft 91, connected' byI-gears 92 and 93 to the main cam the tool' carriage cam 49 sprocket 97 to arshaft 98, whichin turn is connected by gears 99"and 100 to a shaft 101, connected in turn by gears 1'02 and 103 to a second clutch member 104, also loose on the" shaft 88. A rod 105 is slidable axially intheworm shaft 88 but is keyed'theretoby a pin 106.

105 and maybe moved axially thereby to engage either the clutch member 87 or the clutch member .104. Theaxial'position of the rod 105 is controlled by a-cam lever 108 (Fig. 36), positioned by cam plates 109 on the side of a disc 110 on the cam shaft 50.

The cam shaft 50 (Fig. 3) may thus be rotated at relatively high speed during thereturn movement of the tool carriage 44 by engaging the clutch member 107 with the A clutch member 107 is secured on the rod clutch member 87, the driven then being direct.

from the shaft 77 to the worm shaft 88 1 7 through the spiral gears 86. During the operation of finishing the work, the clutch member 107 is shifted to engage the clutch member. 104 and a slow speed drive is obtained from-the work spindle 72 through the sprockets 95 and 97, gears 99 and 100 and gears 102 and 103 to the worm shaft 88.

It will be noted thatthe shift from high to low speed is controlled by the cam plates 109 on the cam disc 110, which in turn is mounted on the main cam shaft 50 and rotates in unison with the carriage cam 49.

The worm shaft 88 is also connected by a sprocket 112, chain 113 and sprocket 114 to a s aft 115'connected in turn by gears 116'and 117 to a worm shaft 118 having a worm 119 engaging a worm wheel 120 on the lower end of a shaft 121 which supports the cam 63 which operates the back tool slide 60.

The driving connections areso proportioned that the back slide cam 63 makes one trolled. The pipe 124 is supplied with air at vfull pressure from the pipe 122, but the pipe 125 15 provided witha reducing valve 126 and thus supplies air at a lower pressure to the mechanism connected thereto. It will be noted that failure ofair pressure in the pipe 122, either by closing the valve 123 or from some accidental cause, will also cause failure of air pressure in the ipes 124 and 125, so that if the clutch 76 1s released, all of the pneumatically controlled devices of the machine will become inoperative, and if the pneumatically controlled devices became inoperative, the main driving clutch will be disengaged. This is an important protective feature.

Work-feeding mechanism Our improved work-feeding mechanism is shown in successive positions in Figs. 4 to 7 of the drawings, and details of the mechanism are shown in Figs. 8 to 16inclusive.

Referring particularly to Fig. 4, the new pieces of work W aremounted on a runway 130, the lower portion of which is provided with a dog 131 controlling the release of successive pieces of work. A fixed lug or projection 132 at the extreme, lower end of the runway stops the released piston in position to be seized and transferred by'the workfeeding mechanism. I

The dog 131 is normally held in the position shown in Fig. 5 by a spring 133 which causes a rearward projection 134 of the dog to engage a cross pin 135. A depending arm 1360f the dog is connected by a link 137 to a lever 138 which is engaged by a tool carriage 44 as it completes its working stroke. Such engagement rocks the dog 131 to release the lowermost piston W or other piece of work. When thus rocked, the rearward projection 134 of the dog swings upward and prevents the escape of more than a single piston.

Details of this holding and releasing mechanism are more fully shown and described in our copending application Serial No. 294,005,'filed July 19, 1928.

i Gripper mechanism- We will now describe the gripper mechanism which we have provided for inserting fresh pieces of work and for removing fin-' ished pieces of work. For this purpose, we provide two pairs of gripping jaws 140 and 141, the jaws 140 acting to feed the work to the machine and the jaws 141 to remove the work from the ,machine. When thus :removed, the work is released on a delivery runway 142 (Fig. 5);

The details of construction of the gripper mechanism are best shown in Fig. 8 and in Figs. 11 to 16 inclusive. The feeding and delivery grippers are identical in construction and a description of the feeding grippers 140 and their actuating mechanism will apply equally to the delivery grippers 141.

The two gripping members 140 are identi-' cal in construction and the pivot lugs 143 thereof overlap in staggered relation, as clearly shown in Fig. 13. A stud 145 extends through'the lugs 143' on thetwo grippers 140 and also through bearin g openings in the lower portion of a gripper supporting member 146. The supporting members 146 for the two pairs of grippers are secured on a rock plate 147 (Fig. 4), the upper end of which is pivoted at 148 to a counterbalanced lever 149, which in turn is mounted on a fixed pivot 150.

A cylinder 151 (Fig. 8) is formed in each supporting member 146 above its stud 145.

. An outer piston 152 is slidable in the cylinder 151 and may be forced downward by admitting air under pressure through a pipe 153 to the upper end of the cylinder 151.

The piston 152 is providedwith a suitable cup packing 154 (Fig. 11) at its-upper end and on its opposite sides is provided with tie pending an d;.outwardlv projecting lugs 155,

engaging abutments 156 on the grippers 140. When the cylinder 152 is depressed, the grippers 140 are moved inward to clamp and hold the work.

A second or'inner piston 158 (Fig.1-5) is slidable in a cylindrical recess 159 in the outer piston 152. A spring 160 is interposed between portions of the pistons 152 and 158 and acts yieldinglyto force the inner piston 158 downward and the outer piston 152 upward.

At its lower end, the inner piston 158 is provided with offset lateral projections 161 (Figs. 15 and 16), positioned to engage projecting surfaces 162 (Figs. 11 and 13) on the grippers 140. i

Vhen there is no air pressure in the pipe 153, the spring 160 moves the outer piston 152 to upper or-inoperative position, and at the same time moves the inner piston 158 clown- Ward, engaging the projections 162 and cansing the grippers 140 to be separated, as indicated in Fig. 11. v

en air pressure is applied through the pipe 153, the outer piston 152 moves downward, as indicated in Fig. 8, closing the gri pers 140 andlat the same time causing tiie inner piston 158 to move upward against the pressure of thespring 160. By thesimple admission or release of air pressure in the pipe 153, we are, thus able to close or open the grippers 140 as desired. By similar control of the air pressure in the pipe 163 the opening and closing of the delivery grippers 141 may be controlled. The pipes 153 and 163 commonly have a joint air supply pipe 164 (Figs. 3 and 4) and are thus simultaneously operated.

rippers to their" successive positions. For t is purpose the rock plate 147 (Fig. 4) is provided with a pin or stud 165 (Fig. 9) ex- I tending through a slot 166 (Fig. 7) in an arm 167 (Fig. 9) mounted to rotate on a horizontal stud 168 mounted in a casing 169 secured to the frame of the machine.

A pinion 170 is also fast on the stud 168 or is fixed to the arm 167, and is en aged by rack teeth 171 (Fig. 7) formed on tile piston rod 172 connected to a piston 173. The piston 173 is slidablein a cylinder 174, mounted in fixed position, and having air pipes 175 and 176 (Fig. 7) connected to the opposite ends thereof.

Suitable mechanism to be described trols the shifting of the connections of the pipes 175 and 176 to an air supply or to the atmosphere, as may be desired.

\Vhen air is admitted through the pipe 175, the piston 173 is moved to the'right, as indicated in Fig. 4, and the gripping members 140 and'141 are moved to workgr'ipping position.

If the pipe 175 is then connected to the exhaust and air is admitted through the pipe 176, the piston is moved to its left hand position, as indicated in Fig. 6, the grippers raising and swinging the work and finally positioning the new piece of work between the head and tail centers and the finished piece of work in deliiery position.

If the air admission is then again shifted to the pipe 175, the piston will be moved to the mid-position shown in Fig. 7 and may be held in such mid-position by admitting air equally through both pipes 17 5 and 176. The

grippers will then be in raised, open and inoperative position, which position they will continue to occupy during the machine operations on the work. The raising and lowering of the grippers simultaneously with the swinging movement thereof is accomplished by passing the stud 165 (Fig. 6) through a med cam slot 180 formed in a plate 181, which constitutes the front face of the casing 169 (Fig. 9). As the stud 165 is caused to traverse the cam groove 180, the pivotal support 148 (Fig. 5) of the plate 147 swings in an are about the pivot 150 s of the counterweight lever 149.

The admission of air to the cylinder 174 (Fig. 7) and also to the gripper cylinders 151 is controlled by cam mechanism to be described. For resent purposes, it may be stated that air is admitted through thepipes 153 and 163 to close the grippers 140' and 141 as soon as the parts reach the positions in:

dicated in Fig. 4, and that the air supply is cut oil and the grippers are released as,

soon as the parts'reach the positions indicated in Fig. 6.

Tail stock mechanism The details of the an stock 42 are best COII- V ward against limit stpvps rock arm 201 swings upon a fixed pivot 202 t and the opposite ends of the rock arm are seated in recesses 203 and 204 in the sliding support 200 and in a plunger 205 respectively.

The plunger 205 is slidable in a suitable fixed bearing and is attached to a piston 206 slidable in a cylinder 207 formed in the tail stock 42 and closed by a threaded cap 208. Pi es 209 and 210 are connected to the cylin er 207 on opposite sides of the piston 206 and either of these pipes may be connected to the air sup 1y or to the atmosphere, as ma bev desired v 1 hen air is admitted throu h the pipe 209, the tail center70'is 'eldingdy advanced to engage the work. 'Wlien air is admitted through the pipe 210, the tail center 70 is withdrawn from the work. 7 An adjustable stop screw 211 engagesa washer 211 which abuts one end of a slidable sleeve 211" which surrounds the plunger 205 and constitutes meansfor tightening the packing in the stuffing box 213 of the lunger205.

he connection 0 the pipes 209 and 210 to the air supply or' to the atmosphere is controlled by cam mechanism to be described.

Work positioning and work driving mecha- 'niam As reviousl stated, the work W'is supported at its c osed or rear end on the tail center 70 and at its 0 n or head end on the conical end of a rotating work support 71, as clearly shown in Fig. 21.

' The inner surface of the end of the piston \V is engaged by a work positionin member 212 (Fi 19 to 21) which is slida l e within a war driving member 214, which in turn is slidable within the work spindle 72, but is ke ed to rotate therewith. The drivin member 214 has a flange 215 engagin a s oulder 216 within the work spin 1e flange 220 engaging the flange 215 of the.

driving member 214 when the latter is in outer position. The flange 220, flange 215 and shoulder 216 thus definitely limit outward axial movement of the work positioning mem- 2 as said member moves. outward,

her 212. The work support 71 (Fig. 19) is axially slidable and is held yieldingly out- 221 by springs 221. A piston rod 222 ig. 19) 15 connected to the member 212 at one end and at the op site end to a piston 224 slidable in a cy der 225 mounted-in the headstock 41. Air

under pressure is admitted to the ends of the cylinder 225 through pipes 226 and 227.

When pressure is applied through the pipe 226, the work positioning member 212 and work driving member 214 are advanced to the the work driving member is projected only far enough, to engage the connecting rod bosses 228 within the piston W, as indicated in Fig. 20, by which engagement the piston W is positively rotated.

The travel of the tail center is controlled by the adjustable stop screw 211 Fig. 18) cooperating with the plunger 205 but this travel is always sufficient to protect the tail center somewhat-beyond the desired working position. The advance of the tail center overcomes and compresses the springs 221 behind thework support 71.

The work positioning member 212 is then advanced toward the tail center and with suiiicient force to overcome the air pressure in the tail center cylinder 207, moving the tail center backward until the positioning member 212 has reached the fixed outward position shown in Fig. 21. The work is thus axially and accurately positioned from the inner surface of the closed end of the piston l)".

It is common to provide higher air pressure in the cylinder 225 in order to effectively overcome the resistance of the tail center 70. The supply of this high pressure air to the cylinder 225 is controlled by cam mechanism to be described.

Pneumatic control mechanism piston valves 231, 232, 233 and 234 (Fig. 26) y are slidably mounted.

These valvesare engaged by rocker arms 235 (Fig. 23) pivoted at 236 and provided with rolls 237 engaged by cams 240, 241, 242

' and 243 (Figs. 31 to 34), said cams being mounted to rotate with the cam shaft 50 previously described. Suitable springs 254 (Fig. 26) are provided for depressing the piston valves 231 to 234. The cams 240 to 243 thus make one revolution 'for each reciprocation of the front tool carriage 44.- The high pressure air supply pipe 124 (Fig.

3) is connected through a passage 250'(Fig. 30) to the valve space controlled bythe piston valve 231. The pipes 226 and 227 (Fig. 3), which supply air to the cylinder 225 for movingthe work positioning member 212, are I connected through passages 251 (Fig. 25) and 252 (Fig. 26) to openings in the casing of the valve 231 above and below the opening 250 previously described. (See Fig. 23.)

)Vhen the piston valve 231 (Fig-30) is raised by its cam 243, high pressure air is admitted-to the pipe 227, and the work positioning and work driving members 212 and 214 are withdrawn. When the cam roll 237 for the valve 231 thereafter engages the low part of the cam 243, as shown in Fig. 34, the

piston valve 231 is moved to its lower position and admits high pressure air to the pipe 226,

thus advancing the work positioning and work driving members 212 and 214 to operative position.

The low pressure (Fig. 3). is connected through suitable branch passages 255 (Fig. 29) to openings 256 (Fig. 26) in the fixed sleeves or bushings in which the valves 232, 233 and 234 are mounted.

The pipes 209 and 210 (Fig. 3) controlling the movements of the tail center are connected through passages 260 and 261 (Fig. 23) to openings through the casing sleeve of the piston valve 232 (Fig. 26) above and below the low premure' opening 255 (Fig. 29) therein. When the valve 232 is raised by its cam 242, low pressure air is admitted to the pipe 210 and the tail center is withdrawn from operative position, but when its cam follower roll 237 engages the lower part of the cam 242, air is admitted to the pipe 209 to advance the tail center 70 and hold the same yieldingly against the work.

The pipe 164 (Fig. 3) controlling the operation of the work grippers, is connected through a passage 270 (Fig. 25) to an opening below the low pressure inlet for the piston-valve 233. As the pneumatic mechanism for the grippers is single-acting, only a sin-. gle air connection is required.

When the cam follower 237 for the piston valve 233 engages the high point of its cam 241, the piston valve 233 is raised to admit low pressure air to the pipe 164 and the rippers are caused to engage the work. When the roll 237 is on the low part of the cam,

the grippers are opened, which is their nor; mal condition during the finishing of the work.'

The pipes 175 and 176' (Fig. 3), which control the movements of the piston 173 which positions the grippers, are connected through passages 280 (Fig. 24) and 281 (Fig. 25) to upper and lower openings in the casing of the piston valve 234. The valve 234 is controlled in its movements by the irregular cam air supply 125' 240 (Fig. 31).- This mi it provided with high spots 284 and 285, a low portion 286,

and an intermediate portion 287.

When the roll 237 is on the intermediate portion 287, the valve 234 will be in midposition. The middle flange or collar portion of the valve is not quite wide enough to cover the low pressure admission port, and consequently the valves 23, when in midposition, will admit air to both pipes 175 and 17 6, thus putting both sides of the piston 173 under pressure and holding the piston from movement in either direction.

' As the cam 240 rotates in the direction of the arrow (1 in Fig. 31, the roll 237 will pass from the intermediate portion 287 to the high spot 284, raisin the valve 234 to admit low pressure air to t e pipe 175, and moving the piston 173 tot-he position shown in Fig.

'4, with the grippers in position to grasp the work.

Further rotation of the cam240. brings the cam follower 237 to the low portion 286 of the cam, reversing the position of the valve 234, and admitting low pressure air to the and holding the parts in the position shown in Fig. 7 until the operations on the inserted piece of :work are completed.

Suitable exhaust connections are provided through which one side of each piston may be connected to the atmosphere when pressure is appliedto the other side. The main exhaust pipe is indicated at 290 (Figs. 22 and 27) and the upper and lower exhaust connections to the piston valve casings are indi-.

cated at 291 and 292 in Figs. 27, 28 and 30'.

When a piston is raised by its control valve, air is admitted to the lower air pipe. controlled thereby and the upper air pipe is simultaneously connected to the exhaust When the piston is lowered, the connections are reversed. Fig. 30" shows the connections for actuating the work driving member 212. The valve 231 is raised, connecting the air supply passage 250 to the pipe 227 and connecting the pipe-226 to the exhaustpipe 290. When thus connected, the member 212 will be withdrawn.

General operation of the machine Having described the details of construction, the general operation 'of the machine will be-readily understood. Assuming that a piece of work has been completed the too slides will be automatically withdrawn andat the same time the gripper mechanism will be moved to work. gripping position. The

tail center will be withdrawn and the work positioning and work driving members in the head spindle will also be withdrawn.

, The grippers will then swing the new work blank to o erative position and the finished work'to dc ivery positioni holding the blank until the tail center an work positioning and work driving members have all been re-' turned. to operative (position. The grippers are then opened an idle or intermediate position, where they remain during the operations on the.insertcd work.

The entire 0 ration of the machine is automatic and t e 'several movements occur in predetermined timed relation and inaccordance with the design and setting of the cams 240 and 243. The provision of pneumatic connections permits a certain amount of yield in case of accidental obstruction to any of the operations, or in case of a variation in the dimensions of the blanks. This is particularl desirable for the gripper are vreturned to t ieir mechanism, w ich frequently grasps blanks v of increased diameten.

The advantages of controlling the main driving clutch from the same air supply as the other operating mechanism have been previously pointed out, this connection preventing operation of any part of the machine if the pneumatic control is out of action.

Having thus described our invention and the advantages thereof, we do not wish to be limited to the-details herein disclosed, otherwise than as set forth in the claims, but what we claim is 1. In almachjne tool' a work feeding device, work supporting devices, work driving devices, a work removing device, and fluid actuated means to operate said devices, and I control mechanism effective to cause actuation of said feeding, work-supporting, and work-dr'ving devices by said fluid, operated means in predetermined timed succession.

2. In" a machine. tool, a work feeding device, a work supporting head, a tail center, a driving device associated with said, head, a work removing device, and automatic means effective to advance said tal center and said driving device to operative positions in predetermined timed relation relative to each other and tosaid work feeding and removing devices, and control mechanism effective to cause actuation of sad several devices by said atltomatic means in predetermined timed succession.

3. In a machine tool, a work-supporting head, a tail center, a driving device associc ntrolling device for said fluid-operated no a means, and control mechanism efiective to cause actuation of said work-supporting head and driving device by said fluid-operated means in predetermined timed succession.

4. In a machine tool, a work feeding device, a work-supporting head, a tail center, a drivin device associated with sa'd head, a tool slide means to reciprocate said tool slide, and fluid-actuated means'efiective to actuate said feeding device and to advance said tail center and said driving device to operat've positions in timed relation to the reciprocating movements of said tool' slide, and control mechanism effective to cause actuation of said feeding, work-supporting and work driving devices by said fluid operated means in predetermined timed succession. v

'5. In a mach'ne tool, a work-supporting" head, a tail center, a driving device associ-' ated with said head, a driving clutch for said machine tool, fluid-operated control means for said clutch, fluid-operated means to ad- 'll vance said tail center and said driving dev co to operative positions, and a single supply of fluid under pressure for said clutch control means and for said means which operates said tail center and said driving device.

' 6. In a mach'ne tool, a work-supporting device, a work driving device, and fluid actuated means effective to operate said supporting device and said driving device, means to supply fluid for moving said driving device a tooperative pos'tion at higher pressure than the fluid for actuating said work supporting device, and control .mechanism efiective to cause actuation of said work supporting and work driving devices by said fluid operated means in predetermined timed success: on.

7 In a machine tool, a work feeding device, a driving head, a yielding work-sup-- porting member mounted therein, a yieldingly advanced tail center eflectiveto overcome the yielding axial. res'stance of said head member, and awork-positioning device movable axiall'v toward said tailcenter to apredetermined operative position as the work is fed, and efl'ective to overcome the yielding axial res'stance of said tail center.

8. In a machine tool, a driving head, a yielding work-supporting member mounted therein, a tail center support, means to move said support and said member yieldinglv toward each other, and adriving device directly engaging'the work and definitelydeteb m'ning the axial position thereof.

'9. In a machine tool, a driving head, a yielding work-supporting member mounted therein, a tailcenter support, means to move said support and said member yieldingly toward each other, and a driving device di rectly engaging the work and definitely deterrmnmg the axial position thereof, said timed succession.

drivin device being more powerfully actuated than said tail center support.

- 10. In a machine tool, a driving head, a yielding work-supporting member mounted therein, a,tail center support, means to move said support and said member yieldingly toward each other, and a driving device directlyengaging the work, and definitely determining the axial position, thereof, said driving device being actuated with sufiicient force to overcome the axial resistance of said tail center support, and astop to limit the axialmovement of said driving device.

11. In a machine tool, work feeding mechanism, work supporting mechanism and work driving mechanism, fluid actuated means (effective to operate said feeding mechanism and to move said supporting and driving mechanisms to operative and inoperative positions, and control mechanism effective to cause actuation of said feeding, worksupporting and work-driving mechanisms by said fluid actuated .means in predetermined 12. In a machine tool, a tool slide, 'worksupporting mechanism, work feeding mechanism,=fluid actuated means to'operate said work feeding mechanism, means tb reciprocate'said tool slide, said means including a driving shaft, and control mechanism efiective to cause actuation of said feeding and worksupporting mechanism by said fluid actuated means in predetermined timed succession.

13. In a machine tool having work-sup.- porting means and work-finishing means, in combination, work-feeding mechanism comprising grippers,'.fluid operated means for actuating said grippers, fluid'operated means for moving said grippers to successive operative positions, and control mechanism effective to control both fluid operated means in timed relation to the operations on the work.

14. In a machine tool, a pair of work gripping tongs, a spring actuated device effective to'separate said tongs, and a device actuated by fluid pressure efl'ective to close said tongs I 1 on the work.

15. In a machine tool, apair of work gripping tongs, a spring actuated device effective to separate said tongs, and a device actuated by fluid pressure effective to close said tongs on the work, said latter device overcoming the resistance of said spring actuated device when closing said grippers.

16. y In a machine tool, a pair of work-griping members, a cylinder, a fluid-operated outer hollow piston slidable in said cylinder and efiectiveto close said gripping members,

I a second piston sli-dable within sald first piston, anda spring mounted between said two pistons and effective to move said second piston to-separate said members.

- 17. In a machine tool, a pair of work-gripping members, a cylinder, a fluid-operated outer hollow piston slidable in said cylinder and efl'ective to close said gripping members, a second piston slidable within said first piston, -anda spring mounted between said two I pistons and effective to move said second iston to separate said members, said spring being overcome by said first piston on apphcation of fluid pressure thereto.

18. In a machine tool, a work holding device, means includin a cylinder and fluid operated piston effective to move said device to work-receiving' and work-delivery positions and to anuintermediateinoperative posltlon, and valve mechanism for said cyhnder and piston, effective to cause selectlve movements of said work-holding device to its several positions.

19. In a machine tool, a work holding device, means including a cylinder and fluid operated piston efl'ectiveto move 'said device to work-receiving and work-delivery posi-' tions and to an intermediateinoperativeposition, and valve mechanism for said cylinder and piston effective to cause selective move ment of said work-holding device to its several. positions, fluid pressure bein to both sides of said piston to ho] said device in intermediate position,

20. In a machine tool, a work holding device, means including a cylinder and fluid operated piston effective to move said device to work-receiving and work-delivery positions and to an intermediate inoperative position, valve mechanism efie'ctive to cause claimed in clainrQl, in which means is provided to limit axial movement of said workdriving and work-positioning members.

2 3. The combination in a machine tool as claimed in claim 21, in which means is provided to limit axial movement of said workdriving and work-positioning members, and in which said work-driving member is moved axially by said work-positioning member.

I 24. The combination in a machine tool as cla med in claim 21, in which means is provided to limit axial movement of said workdriving and work-positioning members, and in which said work-driving member is moved axially by said work-positioning member, but has a lost-motion connection therewith relation. applied by which the in travelof an work-driving member is reduced. 1

25. In a machine tool, a head center and a tail center each yieldingly movable toward the other, and an axiall movable work-positioning member directl engaging an end surface of the work and axially" positioning the work therefrom. 26. Ina machine tool, work supporti devices, means to present the work to sai devices and to remove the work therefrom,

work driving devices, actuating means therefor, and fluid-operated means to render said supporting devices and said presenting and removing means operative in predetermined timed relation.

27. In a machine tool, a work-supporting head, a tail center, a driving device associated with said head, a tool slide, means to reci rocate said tool slide means to advance said driving device, fluid advance said tail center, and controllingdevices whereby said slide, driving device and tail center are moved in predetermined timed -op'erated means to 28. In a machine tool, work-supporting devices including a movable tail center, work resenting and removin devices, work driving means, fluid-o erate means to move said tail center and said work presenting and removing devices, and means to move said work driving means axially in timed relation to the movements of said tail center and work presenting and removing devices.

29. In a machine tool having a work support, a pair of work gripping tongs, a spring actuated device efiectivej to separate said tongs, and a device actuated by fluid pressureefl'ective to close said tongs on thework, and means to move said tongs relative to said support.

30. In a machine tool having a work support, a air of work gripping tongs, a spring actuat device efi'ect ive' to separate said tongs, and a device actuated by fluid pressure effective to close said tongs'on the work, said latter device overcomin the resistance of said spring actuated device when closing said 'ppers', and means to move said tongs relative to said support.

In testimony whereof we have hereunto affixed our signatures. EDWIN R. SMITH.

,- ALBERT scHIN Ez; 

